US5154403A - Power plant suspension device - Google Patents

Power plant suspension device Download PDF

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Publication number
US5154403A
US5154403A US07/631,017 US63101790A US5154403A US 5154403 A US5154403 A US 5154403A US 63101790 A US63101790 A US 63101790A US 5154403 A US5154403 A US 5154403A
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United States
Prior art keywords
strain generating
tubular
bolt
shaped bracket
current
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US07/631,017
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English (en)
Inventor
Shigeki Sato
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
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Nissan Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Assigned to NISSAN MOTOR CO., LTD., NO. 2, TAKARA-CHO, KANAGAWA-KU, YOKOHAMA CITY, JAPAN reassignment NISSAN MOTOR CO., LTD., NO. 2, TAKARA-CHO, KANAGAWA-KU, YOKOHAMA CITY, JAPAN ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SATO, SHIGEKI
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Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/3615—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with means for modifying the spring characteristic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
    • B60K5/12—Arrangement of engine supports
    • B60K5/1283—Adjustable supports, e.g. the mounting or the characteristics being adjustable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/38—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type
    • F16F1/387—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers with a sleeve of elastic material between a rigid outer sleeve and a rigid inner sleeve or pin, i.e. bushing-type comprising means for modifying the rigidity in particular directions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/40—Type of actuator
    • B60G2202/42—Electric actuator
    • B60G2202/424—Electric actuator electrostrictive materials, e.g. piezoelectric actuator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/10—Mounting of suspension elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2401/00—Indexing codes relating to the type of sensors based on the principle of their operation
    • B60G2401/10—Piezoelectric elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2401/00—Indexing codes relating to the type of sensors based on the principle of their operation
    • B60G2401/12—Strain gauge

Definitions

  • the present invention relates generally to an engine (power plant) suspension device and more specifically to a device which can be interposed between a vehicle chassis and a power plant and which can be electrically controlled in a manner whereby the attenuation of vibration which is applied to the vehicle chassis, is improved.
  • FIG. 8 shows a prior art arrangement wherein a cylindrical engine mount 2 is supported on a bracket and operatively connected with a power plant (e.g. a transaxle type arrangement wherein the engine and the transmission are combined into a single unit).
  • the mount comprises a cylindrical outer housing 2a and a tubular member 2b which are interconnected by way of an apertured elastomeric body.
  • a U-shaped bracket supports an elastomeric bush type vibration damping mount on a power unit (ICE plus transmission).
  • the inner tubular member of the damper is mounted on the arms of the bracket by way of a bolt.
  • First and second tubular piezoelectric/electrostrictive strain generating elements are symmetrically disposed about the bolt and housed within the inner tubular member of the mount.
  • a control unit which is responsive to crank angle and engine speed, produces an AC current and applies the same to the first strain generating element. The phase of the same current is shifted by 90° before being applied to the second strain generating element.
  • the voltage and frequency of the AC current are selected in accordance with a predetermined schedule which is based on engine speed and crank angle and which enables the AC currents to be applied in a manner which generate vibrations which tend to negate the vibrations which are transmitted from the power unit to the bolt by way of the arms of the U-shaped bracket.
  • a first aspect of the present invention comes in a mounting device which features: an inner member; an outer member; an elastomeric body operatively interconnected between said inner and outer members; a bracket for supporting said inner member on a vibrating body; and electrically controllable strain generating means disposed between said bracket and said inner member.
  • a second aspect of the invention comes in a mounting device which features: an inner cylindrical member; an outer cylindrical member; an elastomeric body operatively disposed between said inner and outer cylindrical members; a U shaped bracket for supporting said inner cylindrical member on a vibrating body, said inner cylindrical member; and electrically controllable strain generating means disposed between said bracket and said inner member, said strain generating means including an element formed of one of a piezoelectric element and a electrostrictive element.
  • a further aspect of the invention comes in a system which features: a vibrating body; a base; a U-shaped bracket fixedly connected to the vibrating body; a support bracket fixedly connected to said base; a tubular outer member rigidly connected to said support bracket; an tubular inner member connected to said U-shaped member by a bolt which passes through the inner member and legs of said U-shaped bracket; an elastomeric body operatively disposed between said inner and outer members; and electrically controllable strain generating means disposed between said bolt and said inner member.
  • strain generating means comprises first and second strain generating elements which have tubular configurations and which are disposed about said bolt, said first and second strain generating elements having inboard ends which are separated by an inwardly extending projection formed on an inner wall of said first member, said first and second strain generating elements being arranged in an essentially symmetrical manner on either side of said inwardly extending projection and so that the outboard ends thereof are in engagement with the legs of said U-shaped bracket.
  • the present invention further features a source of AC current, the source including control means responsive to parameters which vary with the vibration generated by said vibrating body and which applies an alternating current having a selectively adjustable voltage and frequency to the first strain generating element, phase shifts the same current by 90° and applies it to the second strain generating element.
  • FIG. 1 is a cross-sectional view showing the construction which characterizes a first embodiment of the present invention
  • FIG. 2 is a sectional view as taken along section line II--II of FIG. 1;
  • FIG. 3 is a functional block diagram showing the control concept which is used in the first embodiment of the present invention.
  • FIG. 4 is timing chart comparing the displacement (vibration) characteristics obtained with the prior art with those obtained with the present invention
  • FIG. 5 is a graph showing the strain and electric field relationship which is produced by a piezoelectric-electrostrictive material suitable for use in the present invention
  • FIG. 6 is an elevational view partially in section, which shows the construction which characterizes a second embodiment of the present invention
  • FIG. 7 is a functional block diagram showing the control concept which is used in the second embodiment of the present invention.
  • FIG. 8 is an elevation view showing the prior art arrangement discussed in the opening paragraphs of the instant disclosure.
  • FIG. 9 shows in table form an example of a map which can be used according to the invention.
  • FIGS. 1 and 2 show a first embodiment of the present invention.
  • a vibration attenuating mount 10 basically comprises: an inner tubular or cylindrical member 12, an outer tubular or cylindrical member 14 and an apertured elastomeric body 16 which is fixedly connected between the inner peripheral surface of the outer member 14 and the outer surface of the inner member 12.
  • the mount 10 is supported on a bracket 20 by way of a bolt 18 which is disposed through the inner member 12.
  • the bracket 20 is fixedly connected to a power plant 22 while the outer cylindrical member 14 is adapted to be received in a cylindrical support portion of a bracket which is connected to a vehicle chassis (see element 40 in FIG. 6 by way of example).
  • the bracket 20 has an essentially "U" shape.
  • the bottom or base portion 20a of this bracket is connected with the power unit or plant 22 by way of one or more bolts, not shown.
  • the upwardly extending support legs 20b, 20c of the bracket are formed with diametrically opposed holes through which the bolt 18 is disposed and secured in place by a nut 24.
  • the inner member 12 is formed with a radially inward projecting portion 26 which extends toward but does not contact the bolt.
  • First and second piezoelectric actuators 30, 30a in the form of sleeve-like piezoelectric-electrostrictive elements, are disposed about the bolt 18 and within the inner member 12 in a manner wherein the inboard ends of the elements abut the side edges 28, 28a of the inwardly extending projection 26, while the outboard ends thereof are in engagement with the legs 20b, 20c of the bracket 20.
  • a given amount of clearance is defined between the elements 30, 30a and the members between which they are inserted.
  • the first and second actuators 30, 30a are electrically connected with a control unit 32 and are formed of the type of piezoelectric material which is responsive to external electrical fields and which exhibits large field resistance and non-linear strain/electric field hysteresis characteristics.
  • the actuators can be made of an electrostrictive type of material which exhibits a very small field resistance which proximates quadratic curvature. Disclosure relating to this type of material can be found on page 51 of "Piezoelectric/electrostrictive Actuators" published by the Morikita Publishing company in December of 1986).
  • phase transition temperature (Curie Point) and will be referred to collectively as piezoelectric-electrostrictive ceramics.
  • the control unit 32 is connected with a crank angle sensor 33 and engine speed sensor 34 and arranged to produce control characteristics which are suited to suppressing vibration which are excited by the most predominant type of vibration produced by the engine. In this instance this vibration is assumed to be the second harmonic (generated by four cylinder/four cycle engines) merely by way of example.
  • crank angle sensor 33 alone is capable of also providing the engine speed by determining the change in crank angle per unit time or the time required for a predetermined amount of crank angle change.
  • the primary harmonic is determined from the engine rotational speed and halved. In this manner an AC current having frequency which proximates the axially acting secondary harmonic vibration is applied to the first of the two actuators. The signal is then phase shifted by 90° and applied to the second actuator.
  • the phase of the AC current to be applied to the actuators can be determined using a predetermined timing map (viz., a map which is recorded in terms of crank angle sensor output and engine speed (RPM).
  • FIG. 9 shows in tabled form, an example of a map which can be used to determine the AC current frequency, voltage level and the crank angle time at which the voltage should be applied.
  • the instant embodiment is such as to make use of a suitable algorithm which, as schematically indicated in block diagram form in FIG. 3, detects the engine rotational speed and the crank angle output at stages 1001 and 1002. Determines the frequency of the AC current at stage 1003 using the engine speed and at stage 1004 uses a timing map of the nature shown in FIG. 9 in conjunction with both the engine speed and crank angle signals.
  • stage 1005 the voltage and frequency of the AC current are determined and a signal exhibiting the same is applied to the first actuator 30.
  • the phase of the AC voltage is phase delayed by 90° and then applied to the second actuator 30a.
  • the secondary vibration component or harmonic and higher orders create noise problems.
  • the vibration frequency matches the resonance frequencies of the power plant 22 and bracket 20, the mount per se vibrates and this vibration is transmitted to the vehicle chassis.
  • vibration in the frequency range of (50-500 Hz) tend to be transmitted to the vehicle cabin in a manner which induces reverberation noise therein.
  • the voltages which are applied to the actuators 30 and 30a can be controlled in a manner whereby the resulting axial elongation and contraction of the two actuators 30, 30a can be used to produce vibrations which react against and offset that being applied from the legs 21b, 21c. This of course enables a great reduction in the amount of vibration which is transmitted to the vehicle chassis.
  • FIG. 4 graphically compares the vibration damping characteristics of the prior art with those of the present invention.
  • FIG. 4 graphically compares the vibration damping characteristics of the prior art with those of the present invention.
  • XE denotes the displacement of the engine toward the inner cylindrical member 12 of the damper 10
  • XC denotes the displacement induced by the actuators 30, 3a
  • XR denotes the displacement which results after the actuator induced displacement is added to the bolt 18.
  • XB denotes the displacement of the bracket 20 per se.
  • FIG. 5 is a graph which shows an example of the non-linear relationship which develops between the electric field and the resulting strain when a given piezoelectric-electrostrictive material is used. It will be noted that as the amount of strain which is produced is determined by the applied electric field and is not effected by the orientation of the field, the amount of displacement produced by the actuators can be readily determined by controlling the voltages which are applied. Further, as the response of the actuators 30, 30a varies between a few msec to a few ⁇ sec, the response time can be considered to have a negligible effect on the generation of the target frequency.
  • the actuators are cylindrical and symmetrically arranged between the bolt and the inner cylindrical member 12. This reduces the amount of space required for the same and facilitates engine room layout as compared with arrangements wherein an elongated member is oriented against the vibration to be controlled.
  • FIG. 6 shows a second embodiment of the present invention.
  • This arrangement is basically similar to the first embodiment and differs in that, in order to particularly control the resonance of the bracket 40, which is connected to the vehicle chassis and which supports the outer cylindrical member 14 of the engine mount 10, a strain gage 42 is disposed on the bracket. This gauge directly detects the amount of strain which is developed in the bracket 40.
  • the frequency and magnitude can be used to modify, update and/or supplement the data depicted in the table of FIG. 9 in a manner which enables the amount of vibration which is detected in the bracket to be reduced toward a zero level.
  • the manner in which this type of feedback control can be implemented is deemed to be fully within the grasp of the those skilled in the art of vibration control/computer programming.
  • FIG. 7 shows in block diagram form the conceptual arrangement of the second embodiment. It is deemed that the FIG. 7 is self-explanatory and that the concept and arrangement of the second embodiment will be fully comprehended in light of the above disclosure.
  • the present invention of course is not limited to controlling cabin reverberation noise and can find various application where vibration attenuation/control is required. However, one example where the invention is deemed to find particular application is in the attenuation of high frequency vibrations which tend to occur during vehicle acceleration.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
  • Vibration Prevention Devices (AREA)
US07/631,017 1989-12-25 1990-12-20 Power plant suspension device Expired - Fee Related US5154403A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP1-335678 1989-12-25
JP1335678A JPH03193528A (ja) 1989-12-25 1989-12-25 パワープラント支持構造

Publications (1)

Publication Number Publication Date
US5154403A true US5154403A (en) 1992-10-13

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US07/631,017 Expired - Fee Related US5154403A (en) 1989-12-25 1990-12-20 Power plant suspension device

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US (1) US5154403A (de)
JP (1) JPH03193528A (de)
DE (1) DE4041011A1 (de)
FR (1) FR2656398A1 (de)
GB (1) GB2242956B (de)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5295414A (en) * 1991-04-15 1994-03-22 Kubota Corporation Vibration and noise proofing system for a hydrostatic stepless transmission attached to a transmission case
US5303896A (en) * 1992-11-12 1994-04-19 Sterka William E Model airplane engine mounting system
US5305847A (en) * 1992-09-02 1994-04-26 Chrysler Corporation Dual mode engine/transmission mount
US5374038A (en) * 1993-04-27 1994-12-20 Gencorp Inc. Automotive torque strut bushing
US5730429A (en) * 1993-10-29 1998-03-24 Lord Corporation Decouplers for active devices
US5842677A (en) * 1996-09-26 1998-12-01 Lord Corporation Safetied sandwich mount assembly with integral holding and centering feature
US6068248A (en) * 1996-12-19 2000-05-30 Hyundai Motor Company Power plant mounting bush
US6419214B2 (en) * 1999-09-27 2002-07-16 Uniroyal Chamical Company, Inc. Non-linear spring rate sway bar bushing
US6419215B1 (en) 1999-09-27 2002-07-16 Freudenberg-Nok General Partnership Bi-component bushing
US6459970B2 (en) * 2000-06-19 2002-10-01 Tokai Rubber Industries, Ltd. Control data setting method and data storage medium of active mount control apparatus
US6651966B2 (en) * 2001-06-27 2003-11-25 Carl Freudenberg Kg Aggregate bearing in bushing form
US20050121219A1 (en) * 2003-09-18 2005-06-09 Heiko Pohl Bushing with integrated rotation angle transmitter
US20060039095A1 (en) * 2004-08-20 2006-02-23 Honda Motor Co., Ltd. Actuator drive control device
US20100019424A1 (en) * 2008-07-28 2010-01-28 Gagliano Charles J Mount devices and methods for measuring force
US20140200764A1 (en) * 2013-01-16 2014-07-17 Honda Motor Co., Ltd. Control apparatus for controlling active vibroisolating support device
CN112412753A (zh) * 2021-01-22 2021-02-26 宁波东腾机械制造有限公司 一种使用稳定的汽车空调压缩泵泵壳及其安装工艺和应用

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4116270C2 (de) * 1990-05-18 2002-01-17 Toyo Tire & Rubber Co Dämpfungseinrichtung
JP2743590B2 (ja) * 1991-02-06 1998-04-22 トヨタ自動車株式会社 エンジン振動吸収装置
JPH05169983A (ja) * 1991-12-20 1993-07-09 Nissan Motor Co Ltd パワーユニット支持装置
JP3314484B2 (ja) * 1992-12-28 2002-08-12 株式会社デンソー 車両制振装置
GB2349442B (en) * 1999-04-29 2002-12-31 Draftex Ind Ltd Adjustable damping

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3762671A (en) * 1972-08-04 1973-10-02 Gen Motors Corp Engine mount assembly
DE3214037A1 (de) * 1982-04-16 1983-10-20 Volkswagenwerk Ag, 3180 Wolfsburg Aggregatlager fuer ein verkehrsmittel, insbesondere fuer ein kraftfahrzeug
JPS61220926A (ja) * 1985-03-27 1986-10-01 Mitsubishi Electric Corp 車両の振動制御装置
JPS6392851A (ja) * 1986-10-06 1988-04-23 Mitsui Eng & Shipbuild Co Ltd アクテイブ振動絶縁装置
JPS63203941A (ja) * 1987-02-17 1988-08-23 Tokico Ltd 防振装置
JPS63231032A (ja) * 1987-03-16 1988-09-27 Toyota Motor Corp 流体入りブツシユ
JPS6414522A (en) * 1987-07-03 1989-01-18 Sanyo Electric Co Electronic control type cooker
JPS6444326A (en) * 1987-08-10 1989-02-16 Daihatsu Motor Co Ltd Measurement of engine sharing load
GB2222657A (en) * 1988-09-09 1990-03-14 Topexpress Ltd Active control of vibration
DE3901737A1 (de) * 1989-01-21 1990-07-26 Phoenix Ag Metall-gummi-lager
DE3902605A1 (de) * 1989-01-28 1990-08-02 Continental Ag Elastische lagerung, insbesondere kraftfahrzeug-motorlager

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3762671A (en) * 1972-08-04 1973-10-02 Gen Motors Corp Engine mount assembly
DE3214037A1 (de) * 1982-04-16 1983-10-20 Volkswagenwerk Ag, 3180 Wolfsburg Aggregatlager fuer ein verkehrsmittel, insbesondere fuer ein kraftfahrzeug
JPS61220926A (ja) * 1985-03-27 1986-10-01 Mitsubishi Electric Corp 車両の振動制御装置
JPS6392851A (ja) * 1986-10-06 1988-04-23 Mitsui Eng & Shipbuild Co Ltd アクテイブ振動絶縁装置
JPS63203941A (ja) * 1987-02-17 1988-08-23 Tokico Ltd 防振装置
JPS63231032A (ja) * 1987-03-16 1988-09-27 Toyota Motor Corp 流体入りブツシユ
JPS6414522A (en) * 1987-07-03 1989-01-18 Sanyo Electric Co Electronic control type cooker
JPS6444326A (en) * 1987-08-10 1989-02-16 Daihatsu Motor Co Ltd Measurement of engine sharing load
GB2222657A (en) * 1988-09-09 1990-03-14 Topexpress Ltd Active control of vibration
DE3901737A1 (de) * 1989-01-21 1990-07-26 Phoenix Ag Metall-gummi-lager
DE3902605A1 (de) * 1989-01-28 1990-08-02 Continental Ag Elastische lagerung, insbesondere kraftfahrzeug-motorlager
GB2234318A (en) * 1989-01-28 1991-01-30 Continental Ag Motor vehicle engine mounting

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5295414A (en) * 1991-04-15 1994-03-22 Kubota Corporation Vibration and noise proofing system for a hydrostatic stepless transmission attached to a transmission case
US5305847A (en) * 1992-09-02 1994-04-26 Chrysler Corporation Dual mode engine/transmission mount
US5303896A (en) * 1992-11-12 1994-04-19 Sterka William E Model airplane engine mounting system
US5374038A (en) * 1993-04-27 1994-12-20 Gencorp Inc. Automotive torque strut bushing
US5730429A (en) * 1993-10-29 1998-03-24 Lord Corporation Decouplers for active devices
US5842677A (en) * 1996-09-26 1998-12-01 Lord Corporation Safetied sandwich mount assembly with integral holding and centering feature
US6068248A (en) * 1996-12-19 2000-05-30 Hyundai Motor Company Power plant mounting bush
US6419215B1 (en) 1999-09-27 2002-07-16 Freudenberg-Nok General Partnership Bi-component bushing
US6419214B2 (en) * 1999-09-27 2002-07-16 Uniroyal Chamical Company, Inc. Non-linear spring rate sway bar bushing
US6459970B2 (en) * 2000-06-19 2002-10-01 Tokai Rubber Industries, Ltd. Control data setting method and data storage medium of active mount control apparatus
US6651966B2 (en) * 2001-06-27 2003-11-25 Carl Freudenberg Kg Aggregate bearing in bushing form
US20050121219A1 (en) * 2003-09-18 2005-06-09 Heiko Pohl Bushing with integrated rotation angle transmitter
US20060039095A1 (en) * 2004-08-20 2006-02-23 Honda Motor Co., Ltd. Actuator drive control device
US7915842B2 (en) * 2004-08-20 2011-03-29 Honda Motor Co., Ltd. Actuator drive control device
US20100019424A1 (en) * 2008-07-28 2010-01-28 Gagliano Charles J Mount devices and methods for measuring force
US8267383B2 (en) * 2008-07-28 2012-09-18 Honda Motor Company, Ltd. Mount devices and methods for measuring force
US20140200764A1 (en) * 2013-01-16 2014-07-17 Honda Motor Co., Ltd. Control apparatus for controlling active vibroisolating support device
US9352643B2 (en) * 2013-01-16 2016-05-31 Honda Motor Co., Ltd. Control apparatus for controlling active vibroisolating support device
CN112412753A (zh) * 2021-01-22 2021-02-26 宁波东腾机械制造有限公司 一种使用稳定的汽车空调压缩泵泵壳及其安装工艺和应用

Also Published As

Publication number Publication date
GB2242956A (en) 1991-10-16
GB9027925D0 (en) 1991-02-13
GB2242956B (en) 1993-08-25
FR2656398A1 (fr) 1991-06-28
DE4041011C2 (de) 1993-01-14
JPH03193528A (ja) 1991-08-23
DE4041011A1 (de) 1991-06-27

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